Valve



sept. 2', 1941.

w. M. zAlKowskY VALVE Filed March 30, `1936 8 Sheets-Sheet l FIG. lA

FIG. s

Sept. 2, 1941. w.'M. zAlKowsKY VALVE 8 sheetssheet 2 Filed March 3o, 193e FIG. l-A

FWG. l-A

ATTORNEY Sept 2, 1941- w. M. zAlKowsKY -2,254,340

VALVE Filed March 30, 1936 8 Sheets-Sheet 3 INVENTOR Sept. 2, 1941.

W. M. ZAIKOWSKY VALVE 8 Sheets-Sheet 4 Filed March 30, 1956 sept. l2, 1941.

W. M. ZAI KOWSKY VALVE Filed March 50, 1936 8 Sheets-Sheet 5 Sept 2, l94l w. M. zAlKowsKY 2,254,340

VALVE Filer; March 5o, 193e a sheets-sheet Ves n `ATTORNEY Sept 2, 1941- uw. M. zAl'KowsKY 2,254,340

y VALVE Filed March 3o, 195e e sheets-snaai s BY lu/wu ATTORNEY Patented Sept. 2, 1941 UNITED STATES PATENT OFFICE 41 Claims.

This invention relates to valves for controlling the flow of uids or liquids, and more particularly to valves provided with a plug rotatable through an angle for causing passages or ports in the valve body and in the plug optionally to be in registry or out of registry.

Such valves in general are old and Well-known. For low pressure operation, and for low discharge rates through the valves, no serious dificulty arises in the operation of such valves. The plug is usually tapered and accurately finished to fit into a correspondingly tapered seat in the valve body; and the contiguous tapered surfaces commonly have been used notY only for sealing purposes but also as guiding surfaces for the plug rotation.

However, Ias the fluid pressure or the Valve size, or both increase, serious design problems arise in connection with valves of this character that are to be found in the prior art. 'I'he resistance to opening of the valve increases faster than might be expected. It has not been uncommon to provide very expensive gearing or reduction mechanism to make it possible to rotate the plug as required. The reasons for such increase of the resistance to operation are not completely understood, and consequently the valve designer, encountering such problems,has been led to bulky and expensive modes of applying adequate torque to the plug. Often the increase in mechanical force for the valve rotation (for example by worm and wheel transmission, reduction gearing, motor drive, or combinations thereof), has been supplemented by expensive or complicated devices for lubricating the valve surfaces or for freeing a frozenf plug, or for performing both these functions. f

These design problems encountered and only awkwardly and partially taken into account by valves heretofore constructed or suggested, have been effectively and inexpensively solved by the present invention. v

Resistance to plug rotation is materially reduced by the aid of the present invention. One serious cause` of greatresistance in prior devices is that the plug does not remain truly coaxial in its seat at all times, thus making tipping or cooking of the plug possible. This mlsalinement of the plug in its seat leads to a concentration of contact at localized points on the plug periphstantially at all times, of the plug in` its seat, and thus ensure uniformity of clearance. 'I'his is accomplished by the aid of a sturdy center post, rigidly supported by the Valve body, upon which the closing member or plug is rotatable and, optionally, axially movable as well.

Another cause for increasing the resistance to movement of the plug is the existence of pressure of the iluid, tending to urge the plug in a. direction perpendicular to its axis. This lack of fluid pressure balance is usually most pronounced when the valve is closed, the inlet iluid pressure having a resultant such as to urge the plug toward the seat around the outlet port. This unbalancing is compensated for or' substantially neutralized Vby this invention; particularly by uid pressure operating on the plug or closing4 member in the proper direction to secure substantial side balance.

As a result of maintaining allnement of the plug as well as sidewise balance, it is entirely feasible, with the aid of this invention, to maintain the plug or closing'member in a definite and xed adjustment adequate for satisfactory seal and easy operation of the valve. Of course, a sealing and lubricating material, such as any proper grease or substance, is utilized to ll the residual annular clearance space, if any.

Sealing and lubricating compounds have been used heretofore in grooves located either in the plug or in its seat, or in both, but difculty has been experienced in forcing the compound from the grooves into the spaces Where line uid pressure is apt to form contact between plug and body seat. By the aid of the present invention,

the spread of the sealing and lubricating material produces complete lubrication without waste of said material.

ery, and non-uniform clearance between the plug In lsome instances the lift of the plug from its seat has been used to facilitate its rotation and lubrication. By the aid of the present invention, it is possible to accomplish these results in a novel manner by utilizing uid pressures that are directed to other of the foregoing purposes, suchas to secure side balance.

In order to enhancerthe sealing eiect, it 'is possible, by the aid of this invention, to expand the plug internally by the aid of fluid pressure. so as to urge its sealing periphery toward 'the seat, and yet to secure easy rotation of the' closing member by counteracting the eiect of line fluid pressure by external pressure of lubricant.

By the aid ofthe present invention it is possible to adapt a tapered closing member for utilization have easy operation of the valve.

By the aid of the present invention it is possible to construct a valve in which the members under tension can be conveniently made of forged material. ,y

It is another object of this invention to make it possible to pass a sealing lubricant to grooves adapted to be intermediate the port openings, and yet to ensure that no pressure will be exerted in these grooves during the period when the grooves are exposed to port openings.

This invention possesses many other advantages, and has other objects which may be made more easily apparent from a consideration of several embodiments of the invention. For this vtion is best defined by the appended claims.

Referring to the drawings:

Figure 1 is a diagrammatic cross section of a valve structure, useful in explaining some of the features of the invention, the valve being shown in open position;

Fig. 1A is a diagram similar to Fig. 1, but showing the valve in closed position;

Fig. 2 is a diagrammatic cross section similar to Fig. 1, but of a diierent form of the valve structure, the valve being shown in open position;

Fig. 2A is a diagram similar to Fig. 2, but showing the valve in closed position;

Fig. 3 is a sectional view of a valve structure constructed in accordance with the diagrams, Figs. 1 and 1A;

Fig. 4 is a sectional view of a valve structure constructed in accordance with the diagrams, Figs. 2 and 2A;

Fig. 5 is a longitudinal sectional view of a valve structure in which some of the features of the invention are incorporated;

Fig. 6 is a sectional view taken along plane 6 6 of Fig. 5;

Fig. 7 is a sectional view taken along plane 1-1 of Fig. 5;

Fig. 8 is a sectional view taken along plane 8-8 of Fig. 5;

Fig. 9 is a sectional view taken along plane 9--9 of Fig. 5;

Fig. 10 is a development of the valve body seat surface used in the form of the invention illustrated in Fig. 5, and shows the location of the various ports;

Fig. 11 is a development of the plug surface corresponding to the plug that is adapted to cooperate With the body seat shown in Fig. 10;

Fig. 12 is a longitudinal sectional view of a modified form of the invention;

Fig. 13 is a sectional view of a further modiiication of the invention;

Fig. 13A is a. fragmentary sectional view illustrating another form of the invention;

Fig. 13B is a fragmentary sectional view illustrating a still further form of the invention;

Fig. 14 is a sectional view taken along the plane lll-I4 of Fig. 13;

Fig. 15 is a sectional view taken along the plane |5|5 of Fig. 13;

Fig. 16 is a sectional view takenA along the plane I6|6 of Fig. 13;

Fig. 17 is a sectional view taken along the plane I1-l1 of Fig. 13;

Fig. 18 is a sectional view taken along the plane l8-l8 of Fig. 13;

Fig. 19 is a plan view of a spring washer that can be utilized in connection with several of the forms illustrated;

Fig. 20 is a side elevation, partly in l,section of the washer shown in Fig. 19;

Fig. 21 is a pictorial view of the plug utliized in the form of the invention illustrated in Fig. 13;

Fig. 22 is an enlarged sectional view of a spring pressed valve utilized in connection with several of the forms of the invention;

Fig. 23 is an enlarged fragmentary detail section, illustrating a, form of sealing groove that may be utilized in connection with some of the forms of the invention; and

Fig. 24 is a diagram showing the valve of Fig. 6 in a partly open position.

In the form illustrated in Figs. 1, 1A and 3, the ,valve body 35 is shown as having an inlet port 2 and an outlet port 3. The body 35 forms a tapered plug seat 36 for the accommodation of a rotatable plug closure member 31. This form illustrates a construction in which the line joining the centers of the ports 2 and 3 is spaced from the axis of rotation of plug 31.

Specifically, this form uses a plug closure adapted to rotate through for opening or closing the valve. In other words, radial lines 2' and 3', extending from the axis of plug 31 and passing through the center of the arc corresponding to the openings 2 and 3, form an angle of 120. This type of valve will be designated as a 120 valve. As it has certain distinct advantages over a valve structure in which the center lines of both the inlet and outlet ports pass through the axis of the rotatable plug, a more detailed description of this type of valve will now be set forth.

The plug or closing member 31 is generally of hollow construction, having two wall portions 33 and 33'. These wall portions are joined at the top and bottom of the plug to form the plug body, and the plug is keyed or splined to a rotatable shaft 38. This shaft is journalled in the wall 39 which overlies one end of the valve body 35. Shaft 38 can be provided with a flattened end 40, for accommodating a suitable handle or wrench to impart a force of rotation to the plug 31. The large end of the seat 36 can be closed by a fluid tight plate 4I secured to the body 35, as by the aid of cap screws 42. This plate 4l may also serve conveniently as a bearing support for the lower end of shaft 38.

In Figs. 1 and 1A, legends havebeen included to designate certain angles, corresponding to the angular motion of the plug, as well as the angular extent of the seal, and of the bores or ports. Thus in Fig. 1, the angle 25 corresponding to spacing, refers to the angular separation of the two ports 2 and 3, as measured between the radial l,lines 2 and 3 passing through the centers of `angle in a counterclockwlse direction. In this as a two-way angular valve.

ligure it is seen that the wall 33 overlaps the outlet 3 by an angle bearing the legends Seal 26 and Opening lag 2 1. The meaning of these terms can now beexplained.- The seal 26 is the angle of 'overlap of the wall 33 beyond the edge of the bore 3, lvserving as a sealing angle. It

is apparent also, that on a clockwise rotation from the position of Fig.l1A, the plug 31 must first be rotated through an angle corresponding to the Seal 26 before the valve begins to open. Therefore, the seal 26 corresponds to this opening lag. The closing lag 28, shown in Fig. 1 corresponds to the angular extent of the lbore, as it is apparent that the plug 31 must be rotated in a counterclockwise direction by that angle before the outlet 3 is fully closed.

In the open position of Fig. 1, the center portion of plug 31 is so" formed as to. provide a. bifurcated passage ,for the fluid. Streamlining is eiected by bringing opposite sides ofthis central portion to a narrow edge or wing 43 opposite the centers of the inlets 2 and 3. In both open and closed position, the plug 31 being hollow, the fluid from inlet2 exerts a pressure tending to expand the plug 31, and to urge the Walls 33 and 33 against the corresponding seating surface in the valve body 35. The short radial arrows extending outwardly toward Wall 33, serve to indicate this internal fluid pressure. This expansion assists in maintaining the seal.

'l A third opening, designated by dotted lines 32, could be placed in the valve body 35 intermediate the inlet 2 and outlet 3. In .this way, the valve can be made to function as a three-way valve. If the outlet 3 ilsclosed up, the valve can be used It is apparent from the geometry of Figs. 1 and 1A that if the spacing 25 is 120, the bores 28 corresponding toi the inlets 2 and 3 must each be no greater thany 120 to permit the valve to close. For three-way operation the bores must` be no greater than 60. In two-way operation, it is possibleto make the bores greater than 90; this is a considerable advantage over the usual two-way 180 type of valve. Thus with the bore 28 extending over an angle of 60, the seal 26 is 60, -which corresponds to the angular separation between'adjacent edges of the two bores. If the bores are made 90 in extent, the maximum seal possible corresponds to 120-90, or 30. If a 18.0 spacing were used for the angle 25, and if the bores were made 90 in extent, the seal angle would be reduced to zero. q

-A further advantage is secured in the 120 type of valve due to the fact that the fluid in the hollow plug 31 is in open and closed positions a duct 44, with the inlet 2. In this way the fluid controlled by the valve 2 can always exert a pressure on the large end ofthe member 31 tourge it in a seating direction, if bores are 60 or greater. the small end of the plug 38 in which lubricant can be forced as by a lubricant Afitting Ma, to provide a pressure vcounteracting the fluid pressure in chamber 4I', to facilitate rotation. The fluid .in chamber M is prevented from escaping by the taperedvalve 38,I on the shaft' 38.

It is apparent from the description of this form of valve that the plug 31 is supported in axial position by the aid of the 'shaft 38, and its lower Y position of Fig. 1, the resultant of the fluid presbeing radial with respect to`the center post 38,

in communication with the inlet 2. This is of considerable advantage where the valve is used for the control of liquids having a larger coeiiicient of thermal expansion than the material of the valve. Upon a rise of temperature after closing the valve, no liquid can be trapped inside sures exerted on the inside of the plug is directed downwardly and toward the third opening 32. This can be readily appreciated by considering the pressures or forces acting radially on the inner surfaces of Walls 33 and 33. These forces the horizontal components cancel each other, because the walls 33 and 33' have a vertical plane of symmetry. The vertical components do not cancel, because there, is no yhorizontal plane of symmetry; instead it can be shown that for two asymmetrical openings, placed above the center of the valve, as in Fig. 1, there is an unbalance transverse force downwards. In case the spacing equals this unbalanced transverse force is equal to the pressure acting on the area of the bore and will be designated as the plug equivalent. It exists so long as line pressure is admitted to the plug interior, and its direction cor- The advantages of an adequately rigid central.;

support in combination with a hollow plug can be secured for a two/way valve structure in which the spacing is This form of valve structure is illustrated in Figs. 2, 2A and 4. In this form,

the valve body I has inlet and outlet passages 2- and 3, as well as a tapered plug seat 5, the axis of which is transverse to the passages 2 and 3'. In this instance the larger end 6 of the seat is open. The upper or smaller end may be provided with a bridge 1, to support the upper end of the plug of the plug 31, nor can undue stresses be produced upon the plug by forces due to this increased -temperature Such unusualI stresses encountered with'trapped liquids may force the trapped liquid between the contacting surfaces ofsthe plug and the body and thereby aiect the lubricating or sealing of the surfaces. This is especially dlsadvantageous lf the liquid happens to be corrosive, which would react disadvantageousl'y upon the sealing materials or surfaces.

It is noted that a chamber 4|' is formed bespindle or post 8. 'Ihe tapered rotatable mem- It also has a transverse passage l0 capable of tween the bottom of the plug 31 and the plate 4I.

being alined with inlet 2 and outlet 3 as shown 3, a compression spring I2 may be confined between the bottom of plug 9 and a head 4 on post This chamberv can communicate, as Iby Way 0f 75 3, urging the plug 'axially upwardly. The post AnotherI chamber 4I" is provided at 8 is not keyed to the plug 8. but acts as a rigid central support for it. 'I'he force exerted by spring I2 may be adjusted by nuts I3 engaging the threaded end of the post 8.

Leakage oi line iluid from passage I around the post 8 is prevented by the aid of a center core I4 of the plug 9, appropriately apertured for the reception of the post 8. The plug wall I6 is spaced from the core I4 to provide the bifurcated passage I0 between the inlet and outlet. The core I4 as before, may be streamlined as by the aid of the narrow wings Il. 'Ihis serves to reduce turbulence rand resistance to ow. To increase the effective area of the passage Il. the top and bottom of the plug interior may be enlarged at the center, as indicated at I8.

The spacing 2i Fig. 2) indieates tneangilar displacement of the outlet bore l from the inlet 2. It corresponds to 180. The angle represented by bore 23 is the angular extent of either the inlet or outlet and corresponds also to the closing lag. The opening lag 24 and the seal 22 are indicated in Fig. 2A. 'I'he pitch 20 in this instance corresponds to an angle of 90, and refers to the required rotation of the plug 8 to open or close the valve.

the inlet 2 and outlet 8 must have a bore 28 no greater than 90. Vfor otherwise the outer I6 of the plug 9 would not be able to seal these bores in the 'closed position. When the valve is open as indicated in Fig. 2. the plug 8 is expanded by internal -line pressure. However, in the closed position of Fig. 2A. the line pressure compresses the plug 8- against the outlet I. Furthermore, the plug -e Il is filled with trapped or isolatedline iluid.

In' the open position of Fig. 2, there is no unbalanced component of the line fluid-pressure exerted on plug 8. However, as the valve begins to close, unbalancing immediately takes place in a direction corresponding tothe axis of bore 8: this unbalancing increases 'in proportion to the area of the wall I6 exposed to the line `pressure in the inlet 2.

Referring to Fig. 2A, a portion of seat 5 is left exposed in closed position to the line iiuid trapped in the plug. This objection is avoided in a. 120 type ofvalve illustrated in Figs. 1, 1A and 3, since in that case the'plugwalls Il an'd 83' completely cover the seat surfaceJin both open and closed positions.

'I'he general problems indicated. by the discussion of the valves illustrated in Figs. 1, 1A, 2, 2A, 3 and 4, relating to sealing of the valve in both open and closed positions, and relating to side unbalance are minimized or substantially'nullied by the construction illustrated in Figs. 5 to 11 inclusive. 22 and 23. In this form of the invention, the spacing ofthe bores is 120; andthe bores are shown as having an angular extent of slightly over 60.

The valve body 4s in this instance has a tapered seat 41 transverse to the inlet opening 66 and theV outlet opening 48 (Fig. 6). A third passage 48 is also indicated in Fig. 6, but, as explained hereinafter, it maybe closed so that the valve func- -tions as an angle two-way valve. 'I'he spacing however, is 120 between the bores.

'I'he lower or smaller end of the valve body 45 is formed by a wa1l.6| (Fig. 5). The upper or larger end can be provided with a ange 52. This v ilange serves to support a bonnet 53 having an opening therein to accommodate the hollow extension 64 ofthe tapered plug 16. The extension 64 is shown integral with member 16, but it may be made separate, if desired, from the member and of forged material, and fastened to the top ilange I8 by any appropriate means, as by bolts. In order to provide a iluid tight construction, a packing 46 can be disposed between the ilange 52 and bonnet 53; and packing 54 and gland 55 can be used to render the joint between the extension 64 and the bonnet 53 fluid tight.

In plug valves of this general character, it is preferable to provide a lubricating and sealing material (such as a grease) between the contiguous surfaces of the plug and its seat. However, little or no attention has been paid heretofore to the problem of maintaining the plug truly coaxial in its seat, and thereby ensure that there be uniform clearance between the plug and'its seat for the reception'of the sealing and lubricating material. It has been common in the past for plugs of this character to develop a minute cooking action, which results in unevenand abnormal wear of the valve, and also in the creation of large forces resisting plug rotation. This cocking or tilting action is apt to be more pronounced with valves controlling fluids at high pressure,

and in valves vof large size. Hence the necessity, as stated hereinbefore, for invoking the aid of mechanisms capable of Aexerting large torques upon the valve plug. n In accordance with the present invention, the tendency of theplug to tilt is reduced by the use of a'. rigid center post such as 56 upon which the plug 'I6 is rotatably supported. Added to this feature is a fluid pressure system arranged substantially to counterbalance or neutralize any transverse thrust that develops on the plug due to line pressure; in other words, side balance is attained. Side balance plus adequate center support for the plug reduces the tilting tendency to an inappreciable value. l

With this end in View, the center post 56 may be held rigidly at its bottom end in the wall 5I Its tapered lower end- 51 terminates in a threaded portion 58; 'Ihe end 51 ilts a correspondingly tapered seat 59 in'the wall 5I, and is urged tightly and rmly into its seat by the aid of the nut 6I. In order further to hold the post 56 in fixed position, a key 60 can be' interposed between the seat 56 and the tapered portion 51,

'I8 and 'I9 and intermediate stiiening ribs 80. A

central aperture 66 is provided for the reception of the post 56. Appropriately fastened upon this spider is the tapered tubular wall 8I, of rather thin material. It has appropriate apertures 82 and 83 capable of being'placed in registry with corresponding ports in the valve body 45. The tubular wall 8I can be joined to the spider 18-18-80 as by welding, the welded spots being indicated in general by reference characters 84 and 85. The center core .TI can be made streamlined as heretofore described, to provide the bifurcated passage 63.

'I'he plug I6 with its extension 64 is restrained (in this form of the invention) against axial movement with respect to the post 56- For this purpose the extensin 64 is provided with an enlarged aperture 64' forming a shoulder 6l around the top of the'aperture 66. Between this shoulder and a nut 68 threaded on the free top end of post 56,4 there maybe interposed a ball thrust bearing structure 68. The nut 69 has a tapered and threaded upper extremity 'I0 which is split, and which can therefore be compressed around the threads of post 56 as by the aid of the4 taper nut 1|, to lock nut 69rmly to post 56. The elements 69, 10, and 1| serve to provide a restraint against upward axial movement o'f the plug structure. To restrain the plug structure against `downward axial movement, a ball thrust bearing 12 is shown as engaging the top of post 56. Thisball 12 is located in a recess in a threaded member 13 engaging the internal threads of the extension 64. This threaded member can be adjusted axially with respect to the plug 16, as by an appropriate spanner wrench engaging ,recesses in its top surface. Since the ball 12 rests on top of the post 56, the plug 16 can be moved upwardly against the thrust bearing 68 by turning the threaded member 'I3 inwardly in the hollow extension 64. It`

is thus seen that the thrust bearing 68 prevents upward motion of plug 16 and ball 12 prevents downward motion thereof.

It is possible by proper adjustment of the nut 69 and the threaded member 13 to obtain any desired clearance between the plug 16 and the seatl 41 in body 45.v

Rotation of the plug 16 can be effected by a wrench or the like, engaging the slightly attened surfaces 65 of the hollow extension 64. As explained in connection with Figs. 1, 1A and 3, the plug in a valve having 120 spacing is subjected to a side pressure both in open and closed positions, which corresponds in direction to the radius spaced 120 from each of the openings 82, 83 of the plug. In order to substantially neutralize this side pressure when the valve is open, it is necessary, as explained in connection with Fig. 1, to provide a radial force corresponding in direction and magnitude with. the unbalanced transverse resultant. This can be readily accomplished in connection with the form of the valve shown in Figs. 5 and 6 by the aid of the closed chamber 48, the pressure in which imparts a neutralizing uid pressure on the plug wall 8| when the valve is in open position. The resultant pressure in cham-ber 48 upon the plug is in line, when the plug is in open position with the plug equivalent, and opposed thereto. The creation of this pressure is accomplished by the aid of a duct |33 extending from the inlet pipe |21 to the space 48. The inlet pipe |21 is fastened to the valve body' as by the aid of the ange |26. The intermediate gasket |3| is notched as shown at |36 in order to leave the upper end of duct |33 open to the inlet fluid. Similarly, the gasket |32 between the closure plate 15 and the valve body 45 is also provided with a notch |31 to leave the duct end open to the space 48, Accordingly, there is an uninterrupted passage from the inlet 58 to the space 48.

When the valve is closed, as shown in Fig. 6, the side pressure on plug 16 is not neutralized by the pressure vexisting in space 48, since there is in this position a side thrust alined with the axis of the outlet 49, and chamber 48 is in communication with the interior of the plug. However,

when the valve is open, the port 82 is in aliner.

ment with outlet 49; and port 83 is in alinement with port 58. The wall 8| covers the space 48 and is subjected to the balancing pressure in space 48, and in this way the plug 16 is balanced.

In Fig. 6, the outlet 49 is shown as connected by the aid of a. flange |26 to an outlet pipe |28.

l An intermediate gasket |30 is provided between flange |26 and the outlet pipe. If it be desired to change the valve so that the passage 48 becomes .the outlet instead of passage v49, it is a simple matter to substitute gasket |36 and ange |26 for the gasket |32 and plate 15. In order to provide side balance for the open position 'even with this change from angular to straight operation, other ducts, such as ducts |34 and |35 can loe-provided in the valve body 45; and by appropriate change in the angular positi'on of the two respective gaskets, one or the other of these two ducts can be utilized to connect the closed space 49 with that port 48 or 50, which is chosen as the inlet.

Ducts |33, |34 and |35 have been merely di'- agrammatically illustrated; other ducts hereinafter referred to are also merely diagrammatically shown. The particular manner in which such ductscan be formed in the various parts of the valve structure forms no part of the present invention. Either coring orf-drilling operations might be utilized, with appropriate end plugs if necessary.

As previously mentioned, Fig. 6 shows the valve in closed position; to open the valve, the plug'is turned clockwise as indicated by the arrow through an angle of bringing opening 82 in registry with body passage 49; and opening 83 in registry with sbodypassage 50. In thisposition, the pressure of the line iiuid tends to unbalance the plug by an amount equal to' the inlet pressure acting on an area the size of the plug opening and along a line directed from` the center of the plug .to the center of body passage 48, This, as before mentioned, is termed the plug equivalent and is neutralized by'admitting line ,pressure the pressure therein can only partly balance 'it.

'I'he plug is further unbalanced by portions 219 and 288 of its surface which are now subjected to line pressure. To maintain the plug in balance as it is turned between fully opened posi- 'tion and the end of the closing lag, a shallow recess 211 is formed in its exterior ,surface equal in extent angmarly and axially to tihpdy passage (see Figs. 5, 6 and 11). By th ineens as the plug is turned from full open position the balancing pressure in'chamber 48 is eective upon an increasing area of thev plug surface. Thus'in Fig. 24, pressure in' chamber 48 is effective over theentire area of recessk 211 and neutralizes the:plug equivalent. The pressure also acts on the exposed portion 28| of thelplug surface beyond the recess and balances the resultant of the pressure acting on portions 219 and`28lv pf the plug surface.

When the end of the closing lag is reached,

maximum imbalance of the plug occurs, this unbalan'ce decreasing as the plug is turned tofully closed position, (Fig. 6) when it reaches normal value. This side unbalance is substantially neutralized by the aid of appropriate fluid pressures made effective upon the sealing or lubricating compound used with the valve.

For this purpose, the sealing and lubricating' grease or compound can be forced under pressure into spaces dened bythe aid of the contiguous surface of the plug 16 and body 45. 'Ihe angular relationship of these areas, as will be hereinafter explained, is such as to make it possible to control the direction of the resultant In the embodiment of the invention illustrated in Fig. 5 cavities or recesses are shown as formed in both the plug 16 and body 45, to which cavities the sealing compound or liquid can be led under pressure. In Figs. 10 and 11, the cavities or spaces in the body 45 are indicated by reference characters |42 to |41 inclusive; and in the plug 16, ,by reference characters |48l to |53 inelusive.I `It is there seen that they are symmetrically arranged in angular relation around the axis of the plug 16. I'he body cavities |42 to |41 are located above and below the port openings 48, 49 and 50. The corresponding plug cavities |48 to |53 inclusive are shown'in Fig. 11 as symmetrical around the axis and of the same angular extentl as the cavities |42 to |41. In either open or closed position, the cavities in the body 45 are in alinement with corresponding cavities in the plug 16. In order to balance the pressure on plug 16 in the closed position of responding to the direction of the plug equivalent) should be supplied with material under suflicient pressure to counteract the unbalanced force. This pressure can be produced prior to the opening of the valve by rotation of the screw |68. The cavities |43 andv |46 in the body seat and |49 and |52 in plug 16 are aligned with the outlet of the valve when the valve is in the closed position. This is seen in Figs. 'l and 9.v

Cavities |49 and |52 of the plug 16 are in communication with each other by the aid of the duct |55 in the plug. Accordingly in the alined position 'of Figs. '1 and 9, if fluid pressure is available in either the upper or lower cavities, the same iuidpressure will be available in the other space. Similarly, the other pairs of upper and lower cavities in the plug are connected by plug ducts. Thus cavities |43, |5| are joined by duct |54; and cavities |56, |53 are joined by duct |56.

'Ihe uid pressure from th'e reservoir is conducted into the upper space formed by the cavities |43 and|49 through a Supply duct |69 in plug 16, shown in Fig. 5. This duct leads from cavity |49 upwardly in the wall of the extension 64 and radially to-connect with a groove |63 in the threaded member 13. Thisgroove in turn is connected as by passages or ducts |64 to a chamber |61 in which there is a check valve, and an upwardly directed opening into the sealing compound reservoir. 'I'hus as screw |68 is turned downwardly, fluid from the reservoir can iiow past the chamber |61 and through ducts |64 into duct |69 and tthe plug cavity |46. This communication is maintained for all angular positions of the plug 16. because the groove |63 in threaded member 13 forms a-complete ring; and any variation in axial position of member 13 -does not affect this connection because duct |69 terminates in a wide axial slot in the face of the extension 64.

Sufhcient pressure to balance the side thrust against the seat |15.

caused by the line pressure is intended to be applied by the aid of screw |63, when it is desired to open the valve. The lubricating and sealing material thus utilized for this purpose is also preferably passed to the other spaces formed 120 ly for the purpose of providing an adequate greasing and sealing eiect in the clearance between the plug 16 and its seat 41. However, the fluid pressure in these spaces should be less than that in the spaces |43-|49 and |46|52;

for otherwise the unbalanced side pressure produced by the line uid would not be materially counteracted.

Accordingly, while, there are ducts connecting all` of the spaces, restraining means or check valves are introduced to prevent passage of the compound into the otherl spaces until appropriate balancing pressures have been built up in the spaces |43-|49 and 46|52.

Fluid pressure, obtained by the aid of screw |68, and existing in spaces |46|52 and |43-|49 can be conducted tothe other spaces |44|5||, |41|53, |42-|48 and |45|5| through a passage |1|l (Figs. 5, 8 and 1l) in communication with space |46-|52, past a valve |13 (Fig. 22) into passage |1| in plug 16. This passage |1| branches into passageways |12 (Fig. '1) to extend to the spaces |41|53 and |45|5|. Since these spaces are joined by ducts |56 and |54 to the.corresponding upper spaces |44|50 and |42-|46, it is seen that fluid may enter these upper spaces also, after it passes valve |13.

The valve closure |16 of valve |13 (see Fig. 22) is spring pressed as by the aid of the compression spring |11. In this way the four cavities |444|53, |41-|53, |42-|48 and |45|5| are supplied with iluid reduced pressure only after the balancing pressures in the other two cavities are reached, because spring |11 restrains the compound against passage by urging closure |16 The valve structure |13 is housed in a recess |15 closed by a threaded headless screw |18, which also serves as a guide for the lower end of the spring |11. The threaded headless screw v|18 can be adjusted withinthe threads of the aperture |14 to adjust the force of the spring |11. To facilitate this adjustment, an aperture |89 is provided in wall |5|, in alinement with aperture |14, and can be closed whennot in use by a threaded plug I6 'Ihe arrangement can be such that by appropriate adjustment of the headless screw |16, the

pressure rst exerted by the sealing compound is utilized for balancing the side pressure oi the plug; and after this side pressure is balanced by the aid of cavities |43-|46 and |46-|52, the sealing and lubricating compound is permitted to pass -valve |13 and to emerge finally in the other four cavities described.

The side thrust due to line pressure is thus balanced by the differences in lubricant pressure closed. For this purpose, the screw |13 is turned tional ducts |59 (Fig. '7) for this purpose inthe body 45 can be provided. In this way even when the plug 16 is rotated away from its closed position, so as to destroy registry between the plug cavity |49 and the body cavity |43, the four plug cavities |50, |53, |48 and |5| are left in communication with four body cavities |44, |41, |42 and |45. In addition, since plug cavities |49 and |52 enter into registry with the body cavities |44 and |41 and the plug cavities |48 and enter into registry with body cavities |43 and |46, all of the cavities become connected. In short, all of the cavities are in communication with each other when the plug cavities |49 and 52 pass out of registration with body cavities |43 and |46. In fact this intercommunication of all the cavities |42|53 is established when plug cavities |49-|52 (first receiving lubricant), begin to register with the body cavities |42 and |45 which, in the valve shown, takes place at the 'The lubricating and sealing material flowing.

into the six cavities serves notonly to balance the side thrust but also to spread lubricant over the plug surfaces for sealing.

It is apparent that upon reverse rotation of the plug to close the valve the reverse action takes place, permitting the transverse force actend of the opening \`lag. 'Ihe two connecting Y ducts |59 can lead to a threaded aperture closed by a headless screw |62. Since, as mentioned before, the passage 48 can be chosen as outlet passage instead of passage 49, provision is made to connect any two sets of body cavities together, instead of merely those just described. For this purpose corresponding ducts |51 and |5`8\(Fig. 7) can be utilized. These ducts, however, when passage 49 is the outlet, are normally interrupted by the headless screws 6| having tapered ends closely contacting the bottoms of their correspondingly tapered apertures. As shown in Figs. 7 and 9, the cavities |43,-|49 and |46|52 are isolated from the other cavities and Aducts |12 except through the plug ducts |10 and |1| controlled by the spring-pressed valve |13, Y the screws |6| being tightened to block ducts |5`|v and |58.

Having created a uid pressure directed radially inwards along the axis of the outlet passage 49 by the aid of the cavities disposed above and below that outlet passage, the plug 16 can then be turned by application of a wrench to the extension 64. As the plug turns, the cavities |49 and |52 are turned more and more out of registry with the corresponding cavities |43 and |46. The

uid pressure nevertheless continues to compensate for side unbalance, as long 'as the plug and body cavities overlap. In fact, Jdue to the overlap, the fluid pressure in these cavities is inunequal areas. The' described form shows merely 'l creasingly eiective to produce a balancing force due to the increase in eiective area of the unalined portions of these stationary cavities. This increasing force serves effectively to counterbalance theunbalanced pressure exerted on the surface of the plug exposed to the inlet port 50. y

When the cavities |49 and |52 pass completely out of-registry with the corresponding body cavities |43 and |46, the fluid in these body cavities need no longer t0 exercise any force, because for this position the liiuid pressure in chamber 48 (Fig. 6) takes care of the unbalance and the valve has now turned through the opening lag.

In the open position, plug cavity |53 is in alinement with body cavity |46; and plug cavity |50 is in alinement with body cavity |43. Fluid pressure can now'be exerted in this condition through duct |69, cavity, |49-|42 and by the aid of the connectingv duct |55 to the corresponding lower cavity |45-|52. Thence the other four cavities are 'providedf with o undiminished pressure; through ducts |59 in the body 45 for cavities |41|5| and |44|48; and through ducts |12 in the plug 16 for cavities |46-I5I and |43-|48;

ing upon the plug to remain balanced until the valve is fully closed, provided pressure is applied by screw |68 at the end of the closing lag.

It is obvious that Athe force necessary to balance side thrust can be obtained by unequal lubricant pressure acting on cavities having equal areas, or by equal lubricant pressure acting on cavities of a preferred method.

It will be observed that by means of screws |6| and |62 all ofthe lubricant cavities in the body can be intercommunicated to cause equal lubricant pressures therein. This is desirable when the plug is to be-turned at a time when there is no line pressure and consequently no unbalanced line pressure forcel acting on the plug. It is quite apparent that under such conditions an unbalanced lubricant pressure would be detrimental instead of beneficial. Of course, if desired, equal lubricant pressures on all sides of the plug can also be obtained by adjusting the screw |18 to reduce the force exerted by the spring |11 on the valve, |15 to zero.

It will be observed that the ducts |51, |58 and |59 provide means for intercommunicating the circumferentially spaced lubricant cavities, which means is quite independent of the intercommunieating system provided by ducts |10 and |1| and o valve |13, and either system may be eliminated and certain advantages of the other system still be obtained. 'I'hu's the ducts |51, |58 and |59 can be eliminated and the ducts |10 and |1| and valve |13 can still be utilized to induce lubricant into cavities |41|53 and |45-|5I at a lesser pres- 7) to balance the force of the line pressure on the plug when the latter isl in closed position; and at the same time effect complete lubrication. The plug can be balanced by introducing lubricant into cavities |46|52 alone, either by eliminating ducts |10 and |1| or by blocking them as by compressing the valve spring |11 sufflciently to keep valve |13 closed at all lubricant pressures employed.

Without employing ducts |10 `and |1 I but with ducts |51, |58 and |59, one can selectively supply lubricant to cavities |46|52 only, or to all of the cavities, by closing oropening the screws |6|.

Since the cavities in moving, spread substantially continuous rings of sealing material above and below the ports, axial leakage of the line duid past the plug is eiectively prevented. However, it is preferable to provide against circumferential leakage between inlet and outlet passages as well- Accordingly, longitudinal passages or cavities or grooves are provided for the plug openings 82 and 88. One form of these cavities is illustrated in Fig. 23. It is there seen that cavity or groove |82 is simply a ilat area ground or otherwise formed on the plug surface to a maximum depth of a few thousandths of an inch. 'I'he groovesformed in this manner have several advantages in addition to the Aease of forming them. 'I'he amount of contained lubricant is very small so that when any of the grooves |82, |83 and |84 pas/sesfrom the seal into the body bore, the lubricant expands but slightly due to the release of pressure in the cavity. Therefore, very little of it is scraped oil as the cavity passes the edge of the body port to reenter the seal. Further, the tapered sides of the cavity enable the pressure on the lubricant to produce a wedging action thereon, resulting in a very effective seal. Another advantage of the relatively broad and shallow grooves -is that the lubricant pressure acting in thev cavities formed thereby facilitates the operationv of the valve, since this pressure counteracts the expansion of the plug which might be caused bythe line uid pressure within the plug.

As an additional preventive of axial leakage between the plug and its seat, circumferential sealing grooves 218 and 21| may be formed in the surface of the plug, above and below the passage 63. -'Ifhese extend entirely around the plug and connect the longitudinal grooves |82, |83 and |84.

Thus all of the sealing cavities are in continuous communication with each other, when the grooves 218 and 21| are provided. r

The sealing grooves are supplied with lubricant from the same reservoir as are the cavities for balancing the plug. Figs. 5, 8, 10 and` 11 illustrate how these sealing cavities |82, |88, I 84, `218 and 21| may be supplied with a sealing compound under pressure at'the same time that this sealing compound is supplied to the balancing cavities. For this purpose, one set of the cavities, for example, |42, |43 and |44, in the body 45 is provided with centrally disposed extensions |88,

communication with groove |84, by means ofa Y. duct |9|, and with groove |83 by a duct |98.

line. This advantage is secured by providing one or more ducts, such as |89 which are in permanent connection with the sealing grooves, but which are in connection with a source of pressure only at specific angular positions.

The lubricant from the balancing grooves may also be used to lubricate the center post 58. A special groove 212 may be formed on its surface meeting annular grooves 213 and 214 near its ends (see Figs. 5, 7, 9). Duets 215 which branch from port |58 are in line with these annular grooves, and allow lubricant from port |58 to,

enter the spiral groove 212. As lubricant cannot' reach port |58 except after passing valve |13, it will be plain that only low pressure lubricant will be used on post 58, and that the balancing of the valve will not be effected.

'In order to prevent any material difference in uid pressure above and below the plug 18, a duct 282 can be provided in the plug to connect the upper and lower spaces. Furthermore, in order to ensure that the desired approach of the surfaces between the plug 18 and seat 41 will be maintained, the valve parts, particularly the center post 58, plug 18 and body 45 are preferably made from metals having substantially the same coeillcient of expansion. It is also seen that the angular width of the body and plug cavities should be commensurate with the corresponding bores in order to make it possible to control the balancing forces in accordance with the plug positions. These relative proportions of cavities to the bores are indicated in Figs. 10 and 11. The resultant center of each pair of cavities is preferably essentially coincident with the center of pressure of the respective port. 'I'his allows transverse balancing without tiltof the closing member. This described assembly is particularly adaptable to a slightly tapered or even a cylindrical plug valve.

In the form lust described, the spacing between the inlet and` outlet ports is less than 180. In the form shown in Figs. 13 to 18 inclusive, the inlet port 94 and the outlet port 93 in the valve body 9| are dlametrically opposite and their.

center lines pass through the axis of the rotatable plug |88. In this form the valve body 9| has a tapered seat 92 for the accommodation of the rosages, all three axial cavities |82, |83'and |84, as

well as the circumferential grooves 218 and 21| when such grooves are provided, are in communication with a source of lubricant pressure to keep the valve sealed in a circumferential as well as axial direction. .Soon after the plug 18 is rotated in a clockwise direction to open the valve,

duct |89 is disconnected from its source of supply; thus before these cavities 182, |83 and |84 can extend across portv openings inthe body 45,

supply of` material under pressure isinterrupted.

The duct |89 does not again aline with a lubricant supply cavity `until the plug is in substantially open position. At that time, the lubricant compound is again permitted to ow, and pressure is exerted thereon into the sealing cavities |82, |83, |84, 218 and 21|. J 1

Y It is an important advantageV of this mode of controlling the supply of sealinglubricant, that at no time is any sealing groove exposed toa port during the exertion of pressure on the lubricant; accordingly there is no appreciable waste of lubricant by expulsion of it under pressure into the tatable plug |88 therein. As before the plug |88 is mounted for rotation on a stationary center post 98, supported at its lower end by the body structure. The plug |88 is provided with a winged core portion ||1, having an aperture |81 for accommodating the center post 98, and forming a bifurcated streamlined passage |8.

The manner gin which the center post4 98 is supported is most readily explained in connection with Figs. 13 and 18. The post 98 has a threaded extremity |88 which extends downwardly beyondthe bottom of the body flange. Furthermore, a key or spline |8| is provided for restraining the center post 98 against rotation. This key operates within a slot formed in the supporting boss 98 of the body 9|, as well as in an elongated slot 98 formed in the lower end of center post 98. The threaded extremity |88 is accommodated in a boss |84 formed integrally with a plate |82, maintained in contact with the bottom of the body 9|. It is apparent that by rotation of plate |82, the post 98 may be moved axiallyin either direction, depending upon the direction of rotation. The centerv post 98 is appropriately provided with a head or enlarged portion 99 operating `in a bore l231 formed in the hollow extension |89 of the plug |88. This head 99 can be provided with an intermediate center groove 99 in which packing may, if desired, be disposed.

In order to make it possible to attach the plate |02 in any angular position to the body after it has been rotated to adjust the center post 98 axially, this plate |02 is provided with a series of notches or recesses |03 adjacent its periphery. Through these recesses may pass a number of cap screws engaging threads in the bottom flange of the body 9|.

The head 99 of center post 98 does not act directly upon the plug |06.- Instead there is interposed a spring washer shown in greater detail in Figs. 19 and 20. .This spring washer is accommodated beneath the head 99 and on the shoulder ||0 formed at the bottom of the bore 231 and around the center bore |01. Thus by drawing post 98 downwardly, for example, the spring Washer is compressed anda greater force is created by the washer to urge the plug |06 into its seat 92.

The spring washer construction involves a ring having a lower flange ||2. This lower ange connects to an interior convex portion |2. The upper flange H4 of the ring is turned downwardly at its outer edges to provide a slight clearance between this downwardly turned end and the bottom flange H2. In order to provide Sunicient resilience for the washer, a series of notches |3 can be cut both in the top and bottom flanges. It is apparent that a compressive force acting on the bottom flange ||2 will urge this .bottom ange toward the top flange ||4; and contact is established between the two flanges before the washer is stressed beyond its elastic limit. Accordingly, a definite limit is imposed upon the degree of upward axial movement that the plug |06 can have. The clearance between the upper and lower flanges of washer is made such as to provide a deiinite small annular clearance between the plug and its seat when this plug |06 is raised in the manner hereinafter described.

The body 2| is open at its top, the downward pressure exerted by the spring washer serving to keep the plug |06 in leak proof contact with the body. As before, the extension |09 can be provided with a portion |08 having flattened sur-v faces, for the accommodation of a wrench or the like for turning the plug |06. This extension |09 furthermore accommodates a threaded member 235, which is tightened down upon a seat formed between the bore 231 and the threaded aperture in extension |09.

A consideration of the line pressures shows that in the closed position of Fig. 15, the plug |06 is subjected thereby to a compressive force against the outlet side of the body 9|. In order to render and 1'1, are similarly located adjacent the bottom of the seat 92. Cavities 200 and 202 are joined by duct 2|2. Cavities 20| and 203 are similarly joined by duct 2 I3. In the closed position shown, a side pressure should be exerted in the cavity 20| as well as in the lower corresponding cavity 203. These two cavities are fed with lubricant compound under pressure from a reservoir 2|5 in the threaded member 235. Pressure is exerted on the material in this reservoir by turning down the screw 2|4. Lubricant or sealing compound from this reservoir passes the ball check valve 2|6 located in member 235 below the reservoir 2|5 and leading to the transverse duct 2|1. This transverse duct 2|1 terminates in the annular passage 2|1' around the member 235. One duct 2|9 from that passage leads to a cavity 205 in the plug |06 (Fig. 14) as well as by way of duct 201 in the valve body 9| to a spring pressed check valve 209. This check valve construction is similar to that described in connection with Fig. 22. The spring in this instance is made to be easily opened by uid pressure, or is simply normally open. After the grease or other lubricating or sealing material passes the valve 209,

the duct 2| (Fig. 14), passes the material to the two cavities 20| and 203. Cavity 205 is made of suiciently large angular extent to maintain the duct passages continuous for passing the sealing material for balancing purposes, during the opening lag period, and irrespective of the direction of rotation of the plug |06.

In order to spread the lubricating material over other parts of the seating surfaces and the plug surfaces, the cavities 200 and 202 are likewise fed with lubricant, via duct 2|8, cavity 204 in the plug |06, duct 206, past spring pressed valve 208, and ducts 2|0 and 2 I2 to the cavities 200 and 202. In this instance, however, the valve 208 is appropriately urged to closed position by its spring. Accordingly there is a differential in pressure exerted on opposite sides of the plug |06, to eiect the side balance. The pressures exerted in cavities 204 and 205 substantially balance each other at all times and can be left out of consideration..

. Lubricant can always be forced into cavities 204 it possible to rotate the plug easily for opening the valve, it is clear that there should be a counterbalancing force in a direction from the outlet 93 toward the inlet 94. For this purpose, use can again be made of pressure exerted by a lubricating or sealing material, exerted in cavities formed between the plug |06 and the body 9|. In this instance, depressions are preferably formed in the body seat surface only, to provide the pressure cavities. These cavities are located both above and below the port openings. The two cavities 200 and 20| shown in Fig.' 14 adjacent the top of the seat 92 and diametrically opposed, have an angular extent such that they leave annular gaps equal to the opening lag be- 'tween their end and the end of cavities 204 and 205 in the plug, when the valve is fully closed. The two cavities 202 and 203 shown in Figs. 13

and 205, from which it can flow into stationary cavities 200 and 20| as follows: across check valves 208 and 209 during opening lag, and directly the rest of the time.

After the pressure of the sealing compound is thus made effective to balance the plug |06, this plug can be rotated to open the valve. During the period of opening lag, the cavities 204- and 205 stay in register with the loodsr ducts 206 and 201. Continued rotation to fully opened position maintains these cavities out of register, for when the valve is open even slightly, there is no longer any disturbing side unbalance. When the valve is closed from fully opened position, no balancing pressure need be exerted until the valve begins to close; that is, during the closing lag. At this point in the operation, cavities 204 and 205 are in communication with their ports 206 and 201 so as to render the balancing pressure again eective when screw 2|4 compresses the lubricant.

Since the valve structure is symmetrical, by reversing the relative force exerted by the springs of valve 208 and 209, the inlet 94 and outlet 93 can be interchanged with the samebalancing effect as before.

Longitudinal sealing grooves can also be provided to supplement the circumferential seal provided by the cavities 200 to 205 inclusive. 'Ihese longitudinal sealing grooves 240, 24|, 246 and 241 are illustrated to best advantage in Figs. 15, 16 and 21. They are shown as extending in the center of the sealing surfaces when the valve is in closed position. Grooves 240 and 24| are shown as disposed on opposite sides of the outlet 93; and longitudinal grooves 246 and 241 are shown as on opposite sides of the inlet aperture 94. The arrangement is such that lubricant or sealing material is passed under pressure into the grooves only While the grooves are in juxtaposition to a Wall in the valve body; and only after side balance is attained. As soon as the grooves pass into inlet or outlet port openings, the supply of lubricant is interrupted to the `respective grooves.

This is effected by the aid of diametrically op-V posite cavities and 252 arranged in the periphery of the center post 98 and near the bottom thereof, in conjunction with ducts formed in the rotatable plug |06. Lubricant under pressure can be passed to these two cavities by the aid of the transverse duct 253 connecting with the axial duct 254 in the center post 98. This axial duct in turn connects to a radial extension 254. in register with a horizontal duct 24| in the bottom of the body 9|.

The supply of lubricant to duct 24| .is effected through a narrow horizontal bore 224. This bore is placed intermediate the larger bores 223, 223', and valves 230, 23| control the admission of lubricant from one or the other of the bores 223, 223', in cooperation with their valve seats 225 and 226. The valves are joined by a common center rod 232, so that when communication from one bore to intermediate bore 224 is interrupted, communication from the other is established. The ends of the bores 223, 223 are closed by the headless screws 221.

When port 94 is the inlet port, lubricant under pressure is immediately supplied from the reservoir to cavity 205, and duct 2|3 as heretofore stated; thence into duct 229 and into bore 223. This pressure is immediately effective to urge valve 23| to its seat to the position shown in Fig. 18. The valve 230 however is unseated by this pressure. The intermediate bore 224 is thus placed in communication with the bore 223. Bore 223' is supplied with lubricant through ducts 228, 2I2 and valve. 20B. Thus lubricant can pass through the space 223', the intermedi.

ate bore 224, ducts 24| and 254' to the axial duct 254 and into the cavities 25| and 252; but only after side balancing has been effected.

If port 93 is the inlet port the result is the same except that in that case the valve 230 will create the lifting force is rendered effective through one of the bores 223, 223.

Lubricant under pressure from cavities 25| and 252 in the closed position of the valve can pass to the four longitudinal grooves 240-24|, 246 and 241 by the aid of the radiai ducts 249, 2492.250 and 250' in the plug |06 (Figs. 1 6 and 21). Radial duct 249 connects cavity 25| with the lower arcuate extension 243 of groove 24|. Radial duct 250 connects cavity 25| with the lower arcuate extension 244 of groove 240. Similarly, on the opposite side of the plug |06, radial duct 249 connects cavity 252 with the lower arcuate extension 243 of groove 241; and radial duct 250 connectsthe cavity 252 with the lower arcuate extension 244 of the groove 246. These lower arcuate extensions 243-244, 243' and 244 are overlapped as shown most clearly in Fig. 2l, and form a circumferential and axial seal; thus the port openings are interbracketed by these grooves. rotated in a clockwise direction to open the valve, it is seen that ducts 250 and 250 pass out of registry with the supply cavities 25| and 252 shortly after the turning motion is started. Accordingly grooves 240 and 246 are disconnected from their source of lubricant pressure prior to the time when they enter the port openings. However, ducts 249 and 249 remain in communication with cavities 25| and 252; and therefore grooves 24| and 241 are continually supplied with lubricant under pressure. This is proper because these grooves do not in this opening movement become exposed in the port openings.

It is apparent that upon a counterclockwise rotation to open the valve, the supply of lubricant to grooves 24| and 241 is interrupted; and the supply of lubricant to grooves 240 and 246 is maintained.

It is scmetimesadvisable to create a pressure to unseat the plug |06 slightly before it is rotated. In the form illustrated in Fig. 13, this can be accomplished by the aid of a pair of cavities 258 on opposite sides of the center post 98, similiar to cavities 25| and 252 and adjacent the top of the post. These cavities connect by the aid of radial ducts 256 and 251 (shown most clearly in Fig. 21) with the upper arcuate extensions 242 and 245 of the grooves 24| and 240 respectively. Therefore when lubricant under pressure is passed to grooves 240, 24|, 246 and 241, this lubricant can pass to cavities 258 and thence through the transverse duct 259 and the axial duct 260 to a space 238 above the head 99 of the center post 98. This pressure acts on the bottom of the threaded member 235 to urge it upwardly. This upwardly axial motion, however, isllimited by `the clearance between the flanges of spring washer- I I. Also, this upward pressure cannot be secured until after the plug |06 is sidewise balanced, due to the fact that the lifting pressure is obtained from the sealing grooves.A

The pressure for raising the plug |06 in this manner is effective thereafter through a range of angular motion, by making cavities 258 substantially coextensive with cavities 25| and 252.

Other modifications for raising the plug |06 can be utilized. In the form shown in Fig. 13A, it is intended that the plug |06 have no sealing grooves. Instead, the bore 224 leads directly to an upright duct 233 extending into the space at the bottom of the plug |06. Accordingly', when pressure is exerted by turning screw 2|4, lubricant under pressure can pass to bore 223' after side balance is established, by Way of the duct 228, and thence to the intermediate bore 224 to the duct 233 to exert an upward pressure.

1n the form shown in Fig. 13B, the lubricant' pressure is exerted at the top of the head 99 by way of the axial duct 239 connecting with the radial duct '24| supplied from the bore 224 as before.

If it be assumed that the plug |06 is Of course in both of these modifications the `upward movement isiimited by the free relative movement of the flanges of the spring washer In the form shown in Fig. 13B, the space 238 being quite small, little lubricant is needed to initiate the plug lift.

It may sometimes be advisable to provide lubricant pressure to urge the plug toward its seat instead of away from its seat, and to employ a mechanical lift arrangement when necessary to free the plug from its seat. Such an arrangement can be used in lieu of, or in addition tothe spring washer III or its equivalent, in order to compensate for the vertical component of the line pressure against the tapered plug surface. This form is shown in Fig. 12. Ir this embodiment the head 99 of the center post 98 is shown as provided with a seat for the ball thrust bearing |20 which is in contact with a seat in the bottom of the threaded member I 2|. This member |2| can be provided with a ilatted portion |22 for facilitating its operation. By turning the threaded member down in the extension |08, the plug can be raised. The balancing cavities 200, 20|, 202 and 203 can be arranged to be supplied with lubricant under pressure as before. The sealing grooves can, as before, be provided with lubricant under pressure through the arcuate extensions 242, 242', 243, 243', 244, 244', 245 and 245 of the sealing grooves. However, these sealing grooves now pass lubricant under pressure to the cavities 258, thence to the cross duct 259 and the axial duct 260, to the transverse duct 26| below the head 99. There the fluid is effective to assist the force exerted by the spring washer to urge the plug |06 toward its seat. The proportions of the valve shown in Fig. l2 are slightly different from those of the valve shown in Fig. 13.

What is claimed is:

1. In a valve structure, a valve body having an inlet and an outlet, a rotatable-closure member therein having ports corresponding to the inlet and outlet for optionally opening and closing the valve by appropriate rotation of the said member, said body and said member having, at their contiguous surfaces, a plurality of spaces divisible into two groups symmetric to and respectively adjacent to and in opposition to the body outlet,

for the accommodation of a pressure transmitting medium isolated from the fluid controlled by the valve, and means for passing said medium into said spaces, and for controlling the relative pressures of the medium in the respective spaces, whereby the resultant .transverse force of the fluid controlled by the valve upon said member is substantially neutralized by the transverse force exerted by said medium.

2. A valve comprising a. body member having a line fluid passageway therethrough and a tapered seat formed transversely of the passageway, a tapered closure member engaging said seat and having a line fluid passageway extending therethrough adapted to register'with said body passageway in open valve position, a center post coaxial with said seat and extending past the top and bottom walls of said passageway in the closure member, said post being supported by said body member at the end adjacent the small end of said tapered seat against axial movement toward the large end of said seat, and means engaging the other end of the post to the closure member for positively restricting relative axial motion of said closure member with respect to said other end of said post toward the largeend of said seat, the engagement between said post and said closure member being located above the top wall of the closure member, whereby the axial forces transmitted from the body through the center post and the closure member to maintain the seating surface of theclosure member against the seating surface of the body member places the center post in tension and places in compression that portion of the closure member defining the lateral walls of said passageway therein.

3. In a valve structure, a body member having a tapered seat and a line fluid inlet passage and -a line iluid outlet passage intersecting said tapered seat at points spaced substantially apart about the axis of said seat. a tapered closure member engaging said seat and having a passage therethrough adapted to register with both said body passages in open valve position and with the inlet passage in closed valve position, means for applying pressure existing in the inlet passage to the large end of said `closure member throughout rotation of the closure member between fully open and fully closed positions. respectively, comprising a port in the closure member connecting the passage therethrough with the larger end thereof,- and means defining a chamber at the small end of the closure member in which fluid other than line fluid can be forced to provide a Ipressure counteracting the line fluid pressure on the large end of the closure member, to facilitate rotation. g

4. In a, valve structure, a valve body, a. rotatable closure member seated therein, a center post upon which said member is guided, said body and member forming a cavity of angular extent varying with movement of the plug where fluid pressure can be exerted to balance the resultant transverse force due to the fluid controlled by the valve, means whereby fluid pressure may be utilized to lift said member from its seat, and means ensuring that substantial side balance is effected prior to the lifting of said member.

5. In a valve structure, a valve body. a rotatable plug seated therein, said body and plug forming a cavity where fluid pressure can be exerted to balance the resultant transverse force due to the fluid controlled by the valve, said cavity including arcuate recesses in both the body and the plug and of such angular extent that during rotation of the plug between limits, the recesses form an annularly extended cavity, and means for supplying a pressure transmitting mediumv isolated from the fluid controlled by. the valve into said cavity. i

6. In a valve structure, a valve body having an inlet and an outlet. a rotatable closure member therein to control a line fluid, there being recesses between the body and the closure member for receiving lubricant adapted to exert pressure on said member, said recesses varying in eil'ective area during the rotation of said member to open or close the valve, and means to pass lubricant into said recesses to balance the transverse force of the line iluid upon said member during the opening lag.

7. In a valve structures valve body having an inlet and an outlet port. a transversely rotatable formation of said member resulting from pres sure therewithin contributing to the seal. and means utilizing lubricant under pressure to cause opposite radial deformation of said member to facilitate its rotation.

8. In.a valve structure, a valve body, a tapered valve plug rotatable in said body, said body and plug having cooperating sealing surfaces and the body having line fluid passages communicating with said sealing surface therein and the plug having a fluid passage therethrough adapted to register with said line fluid passages in open valve position, said plug having an axial passage therewithin, a center post extending into said axial passage and secured against axial motion with respect to said body in a direction toward the small end of said plug, and means for applying force between said post and said plug to effect longitudinal jacking movement of the plug.

9. In a tapered plug Valve, a body having a seat and having inlet and outlet passages transverse to said seat, a plug member having a port adapted to register with said body inlet and outlet passages when the valve is in open position, said body and plug members having an axial hole to receive a shaft, a shaft in said hole, and means utilizing lubricant under pressure to exert an axial force on said plug member to unseat it, said shaft being closely fitted to said plug at at least two substantially spaced axial points whereby the shaft maintains the plug in alignment with the body when unseated, and means for applying pressure fluid independent of line fluid to said plug in such direction as to balance the radial force exerted by a line fluid on said plug, said shaft preserving alignment of said plug in said body, and said means for applying pressure fluid reducing the disaligning forces applied to said shaft.

10. A valve comprising a valve body, a valve plug rotatable in said body, said body and plug having cooperating sealing surfaces and the body having line fluid passages communicating with said sealing surface therein and the plug having a fluid passage therethrough adapted to register with said line fluid passages in open position of the valve, said plug having a cylindrical passage extending axially therethrough out of communication with said fluid passage therein, a stationary center post fitted in said axial passage and anchored to said body, said plug being rotatable on said center post and having lubricant ducts therein extending from said center post passage, means on said post for defining a stationary port registering with said duct in predetermined position of said plug, and means for supplying lubricant under pressure to said port.

11. A valve structure comprising a valve body, a. valve plug rotatable in said body, said body and plug having cooperating sealing surfaces, and the body having line fluid passages communicating with said sealing surface therein, and the plug having a fluid passage therethrough adapted to register with said line fluid passages in open position of said valve, said plug having a. longitudinal partition wall rigidly interconnecting the end portions thereof and dividing said fluid pas- .sage in the plug into distinct passages, and the circumferential walls of the plug being of substantially uniform thickness, means for lubricating said valve including recesses disposed above and below the line fluid passages, respectively, and duct means within the confines of said partition wall for interconnecting said recesses.

12. In a valve structure, a valve body, a valve plug rotatable in said body, said body and plug having cooperating sealing surfaces and the body having line fluid passages communicating with said sealing surface therein, and the plug having a fluid passage therethrough adapted to register with said line fluid passages in open position of said plug, said plug consisting of a circumferential shell of substantially uniform radial thickness, and a separate inner member of different material joined thereto and constituting, with said shell, the walls of said fluid passage through said plug.

13. In a valve structure, a valve body, and a plug rotatable therein, said body and plug having cooperating sealing surfaces and the body having fluid passages communicating with the sealing surface therein and the plug having a fluid passage therethrough adapted to interconnect the body valve passages in open position of the valve, said body and plug defining at least two circumferentially spaced pressure cavities therebetween symmetrically disposed with respect to said body fluid passages when the valve is in closed position, a source for supplying fluid under pressure, and means for supplying pressure fluid from said source to different circumferentially spaced pressure cavities at predetermined different pressures.

14. In a valve structure, a body member, a rotatable closure member therein, the body member having an inlet and an outlet passage and the closure member having a passage therethrough registering with the body passages in the open position of the valve, one of said members having a pair of separate grooves bracketing a body passage when the valve is in closed position and each groove including an arcuate portion substantially coextensive arcuately with said body passage, which arcuate portion merges into a longitudinal portion at one end, said longitudinal portion being substantially coextensive longitudinally with said body passage, and means for separately supplying lubricant to each of the grooves of said pair of grooves.

15. In a valve structure, a body member having an inlet passage and an outlet passage, a rotatable closure member in said body member to control line fluid flow between said inlet and outlet passages, said body and closure members having cooperating sealing surfaces defining cavities isolated from line fluid, and means for applying a fluid isolated from line fluid to said cavities under pressure, said cavities being so positioned, circumferentially, that the pressure fluid therein exerts a resultant transverse force on the closure member directly opposing the force exerted by the line fluid thereon throughout rotation of said closure member through the opening lag.

16. In a valve structure, a valve body having an inlet passage and an outlet passage, a rotatable closure member therein to control line fluid -fiow between said inlet and outlet passages, a

source for lubricant under pressure, and means for distributing lubricant from said source to the mating surfaces between said body and said member, including pressure-reducing means adapted,`in a predetermined position of the member, to build up a resultant transverse lubricant force on said member.

17. In a lubricated plug valve, means to apply lubricant under pressure to two spaced apart portions of the sealing surface of the plug, and means for restraining flow of lubricant to one of said surface portions to reduce the pressure of lubricant at that portion relative to the lubricant pressure at the other portion and produce a predetermined transverse force on said plug. 

